US3765690A - Composite seal - Google Patents

Composite seal Download PDF

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Publication number
US3765690A
US3765690A US00108279A US3765690DA US3765690A US 3765690 A US3765690 A US 3765690A US 00108279 A US00108279 A US 00108279A US 3765690D A US3765690D A US 3765690DA US 3765690 A US3765690 A US 3765690A
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United States
Prior art keywords
annular
composite seal
seal according
face
reciprocating
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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US00108279A
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English (en)
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W Sievenpiper
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Scott Technologies Inc
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ATO Inc
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Assigned to FIGGIE INTERNATIONAL INC. reassignment FIGGIE INTERNATIONAL INC. CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). EFFECTIVE JUNE 1, 1981. Assignors: A-T-O INC.
Assigned to FIGGIE INTERNATIONAL INC. reassignment FIGGIE INTERNATIONAL INC. MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE DATE: DECEMBER 31, 1986 Assignors: FIGGIE INTERNATIONAL INC., (MERGED INTO) FIGGIE INTERNATIONAL HOLDINGS INC. (CHANGED TO)
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/56—Other sealings for reciprocating rods

Definitions

  • the softer member has total memory coupled with a quick response to accept se- 250 vere deflection of the reciprocating member and the harder member, capable of enduring higher pressures, References Cited I serves as a back-up for the softer member to prevent UNITED STATES PATENTS extrusion.
  • the softer member moves relative to the 2,914,369 11/1959 Hayman 92/242 harder WP unde? iligh Pressures i f 3,254,398 6/1966 Herbenar at all.
  • a rod 7,335 8/1954 Bowerman 277/205 wiper can be combined with the harder member, and 3,271,038 9/1966 Bastow 277/205 the harder member can be elongated f d d bear- 3,606,356 9/1971 Beroset 277/190 ing capability FOREIGN PATENTS OR APPLICATIONS 1,019,523 2/1966 Great Britain 277/205 14 Chums 10 Drawmg F'gures Patented Oct. 16, 1973 2 Sheets-Sheet 1 I NVEIYTOR. wan"? SKveWpcpGI' I BY ATTORNEYS Patented Oct. 16, 1973 v 3,765,690
  • COMPOSITE SEAL BACKGROUND OF THE INVENTION This invention relates to seals for hydraulic actuators and, more particularly, to a new and useful rod seal of composite design.
  • a primary object of this invention is to provide a seal for hydraulic cylinders which will remain leak-free under high pressure conditions and which has an extremely long useful life.
  • Another object of this invention is to accomplish the foregoing with a seal having the ability to accept severe rod deflection and which exhibits total memory and quick response.
  • Still another object of this invention is to accomplish the foregoing with seal members which can be readily molded of available materials so as to provide a practical solution to the above-noted problems encountered in the prior art.
  • the composite seal of the present invention is characterized by the provision of a pair of annular sealing members captively disposed in an abutting relation about a piston rod or other tubular element, the members being formed of materials having different hardness characteristics.
  • the softer member has total memory and a quick response in order to accommodate rod deflection without leakage.
  • the softer member Under high pressure conditions, the softer member is forced against the harder member and caused to stretch radially to relieve the bearing pressure between the softer member's sealing lip and the outer surface of the rod, and the compression between the members loads the harder member to increase the bearing pressure of the harder members sealing lip against the outer surface of the rod effecting a tighter seal therebetween to better withstand high pressures.
  • FIG. 1 is a side elevational view, partially in section, of an hydraulic cylinder incorporating the composite seal of the present invention, the intermediate portion of the cylinder being broken away for ease of illustration;
  • FIG. 2 is a fragmentary sectional view, on an enlarged scale, showing the composite seal of this invention as it would appear under a relatively high pressure condition;
  • FIG. 3 is a fragmentary cross sectional view, on an enlarged scale, of one of the members of the composite seal of this invention
  • FIG. 4 is a fragmentary cross sectional view, on an enlarged scale, of the other member of the composite seal of the present invention.
  • FIG. 5 is a front elevational view of the seal member of FIG. 3.
  • FIG. 6 is a rear elevational view of the seal member of FIG. 2;
  • FIG. 7 is a front elevational view of the seal member of FIG. 4;
  • FIG. 8 is a rear elevational view of the seal member of FIG. 4;
  • FIG. 9 is a fragmentary sectional view similar to that of FIG. 2 but on a larger scale and showing the composite seal of this invention as it would appear under a relatively low pressure condition;
  • FIG. 10 is a fragmentary sectional view, on an enlarged scale, of another form of the present invention as it would appear under a relatively high pressure condition.
  • FIG. 1 a double acting hydraulic cylinder, generally designated 10, of the telescopic type including a cylindrical casing 12 and a plurality of concentric, hollow piston rods 14 (which also can be of solid section), 16 and 18 disposed in telescopic relation.
  • Rods 14, 16 and 18 are adapted to be axially reciprocated relative to each other and to casing 12 and are connected at their inner ends to suitable pistons (not shown) in a manner well known in the art. Pressure is successively applied to the pistons to extend and retract their respective rods sequentially in stages starting from the innermost rod 14 and working radially outwardly.
  • Housing 12 terminates at one end in an eye 13 for mounting or otherwise securing cylinder 10 to a suitable support.
  • the other end of housing 12 is provided with an annular collar 20 welded onto housing 12 as at 22.
  • Annular collars 24 and 26 are provided on the distal ends of rods 16 and 18 and are secured thereto as by means of welds 28 and 30.
  • the outer end of the innermost rod 14 is threaded or otherwise attached to an eye member 32 adapted to be connected to a mechanical load.
  • collar 24 surrounds piston rod 14 and is provided with an annular groove or cavity 40 for receiving a sleeve bearing 42 in contact with piston rod 14.
  • Another annular groove or cavity 44 axially spaced from groove 40 is provided in collar 24 for receiving the composite seal 46 of the present invention as will hereinafter be more fully described.
  • a third annular groove or cavity 48 axially spaced from groove 44 is provided in collar 24 for receiving an annular rod wiper 50 held in place by means of a retaining lip 52 formed in groove 48, such wiper 50 being effective to scrape and wipe rod 14 clean.
  • Rod wiper 50 is described in greater detail in pending application Ser. No. 8,175 filed Feb. 3, 1970, to which reference can be made.
  • seal 46 is comprised of a pair of annular sealing members, hereinafter referred to as a low pressure member 54 and a high pressure member 56 disposed in groove 44 to provide a fluid tight seal between adjacent piston rods 14 and 16.
  • Low pressure member 54 is composed of a resiliently yieldable synthetic plastic material and comprises an annular body 58 (FIGS. 3, and 6) having a generally planar axial end face 60.
  • Body 58 is formed at its opposite end into a first annular flange 62 and a second annular flange 64 extending outwardly from body 58 in a slightly divergent relation and joined together at their inner ends to form a cup-shaped cavity 66.
  • Flange 62 extends generally axially from body 58 and has an inner circumferential wall comprised of a straight axially extending portion 68 and an inclined portion 70 extending slightly radially inwardly of portion 68 and terminating in a sealing edge or lip 71 which has an interference fit with rod 14.
  • Flange 62 has an outer circumferential wall 72 extending generally parallel to the inclined portion 70 and an end face 74 joining inclined portion 70 to outer wall 72 and extending in a direction generally normal thereto.
  • Body 58 has an inclined cam surface 75 extending upwardly at an angle from the inner end of straight portion 68 to the inner end of end face 60.
  • Flange 64 extends outwardly from body 58 and has an inner circumferential wall 76 inclined relative to the axis of body 58 so as to extend slightly radially outwardly from body 58. Flange 64 also has an outer circumferential wall 78 generally parallel to wall 76.
  • Body 58 is provided with an outer wall 80 generally parallel with the axis of body 58 and from end face 60 and terminating at the inner end of wall 78.
  • Wall 78 of flange 64 terminates at an annular lip 82 formed between wall 78 and an inclined end face 84 of flange 64.
  • the inner end of end face 84 joins the inner wall 76 at substantially a right angle.
  • the thickness of flange 64, measured between wall surfaces 76, 78 is on the order of one-half the corresponding dimension of flange 62.
  • High pressure member 56 comprises an annular body 86 (FIGS. 4, 7 and 8) and also is composed of a somewhat resiliently yieldable synthetic plastic material but of a higher durometer rating than low pressure member 54.
  • Annular body 86 has a radial end face 88, an outer peripheral wall 90 and an inner wall 92 extending substantially parallel to wall 90 and to the cylinder axis.
  • Inner wall 92 terminates in an inclined portion 94 extending slightly radially inwardly of inner wall 92 to form a sealing edge of lip 96 having an inside diameter of slightly lesser extent than the diameter of inner wall 92.
  • Body 86 has an annular abutment shoulder 98 generally parallel to end face 88 and normal to outer wall 90, and an end face 100, also generally parallel to face 88.
  • An inclined surface 102 extends downwardly at an angle from the inner end of shoulder 98 to the outer end of face 100; the inner end of which joins wall portion 94 to form lip 96.
  • This inclined surface 102 serves as a seat on which low pressure member 54 rides when the two pressure members are axially compressed together by pressure fluid, as will be described.
  • the low and high pressure members 54 and 56 preferably are molded each of integral, one piece construction, to the shape shown in FIGS. 3 and 4 in any size desired.
  • a suitable synthetic plastic material for member 54 is urethane having a durometer rating of about 80.
  • High pressure member 56 also can be formed of urethane but of a higher durometer rating and impregnated with a filler, such as glass fibers for example, to increase the hardness thereof for reasons which will become apparent. While the specified urethanes are presently believed to be preferably, it is recognized that other synthetic plastics exhibiting the necessary characteristics can be utilized.
  • Composite seal 46 is captively contained within annular groove 44 which is concentric with the axis of piston rod 14 and has a generally rectangular cavity configuration in radial section.
  • Groove 44 is defined by an inner annular wall 104, and a pair of axially spaced end walls 106 and 108 disposed in planes perpendicular to the axis of rod 14.
  • Sealing members 54 and 56 are fitted into groove 44 in operative position within hydraulic cylinder.10 and initially assume the low pressure condition shown in FIG. 1. Specifically, high pressure mem ber 56 is disposed in groove 44 with end face 88 engaging end wall 108, the outer wall 90 engaging wall 104 and the inner wall 92 resting against rod 14 with lip 96 in sealing engagement with rod 14.
  • Low pressure member 54 is disposed in groove 44 with inclined surface resting on inclined surface 102 of member 56, inclined portion 70 of flange 62 engaging rod 14, and portions of flange 64 engaging wall 104 and 106, respectively.
  • a slight clearance exists between face 60 and shoulder 98 of members 54 and 56 and between the outer wall of member 54 and groove wall 104 under low pressure conditions to provide axial and transverse or circumferential clearance for movement of low pressure member 54 relative to member 56 under high pressure conditions, as will be described.
  • Lips 71 and 82 of flanges 62 and 64 are in sealing contact with rod 14 and groove wall 104, respectively, and both members 54 and 56 are in sealing engagement about the surface of rod 14.
  • a significant feature of this invention is the provision of low pressure member 54 formed of a relatively soft i.e. more readily yieldable material having substantially total memory or resistance to permanent set coupled with a quick response to its original shape when the distorting force is relieved. This is important in order to accommodate severe rod deflection caused by mechanical loads acting on the outer end of rod 14, without leakage.
  • member 56 has good memory, its response is slower due to the harder material of which it is composed, rendering it susceptible to leakage during rod deflection if used alone.
  • the quick response of member 54 and its dynamic seal lip 71 precludes such leakage. Sealing engagement of lip 71 against rod 14, caused by the interference flt therebetween is augmented by the action of pressure fluid in cavity 66, and is maintained even under severe distortion.
  • member 54 which is on the high pressure side of the seal, is moved by the pressure fluid axially rearwardly against shoulder 98 of high pressure member 56.
  • body 58 is deflected radially outwardly by the camming or wedging action of surface 102 until outer wall 80 of member 54 engages groove wall 104.
  • High pressure member 56 formed of a harder synthetic plastic material, serves as a back-up for the softer member 54 and prevents extrusion of the softer member 54 between collar 24 and rod 14. As the member 54 is forced against and onto member 56, to the position shown in FIG.
  • the softer member 54 is deflected radially outwardly, enlarging the inside diameter thereof and partially relieving the bearing pressure or frictional force between lip 71 and the outer surface of rod 14. This is a particularly significant feature of the present invention because it reduces wear on the sealing lip 71 of the softer member 54 thereby prolonging the useful life thereof.
  • high pressure member 56 is loaded by member 54 to increase the bearing pressure of lip 96 against the outer surface of rod 14 effecting a tighter seal therebetween capable of withstanding high pressure conditions. Therefore, seal member 56 becomes most efficient under high pressure conditions.
  • High pressure member 56 can have a retainer shoulder like that shown on wiper 50, and cavity wall 104 can be formed to receive the same, but wall 108 is of such depth that an additional retainer usually will not be necessary.
  • FIG. illustrates another form of the invention in which the rod wiper is combined with the high pressure sealing member as an integral, unitary part thereof.
  • high pressure member 56' is formed at the end thereof opposite low pressure member 54 to provide a rod wiper portion comprised of a pair of annular flanges 110 and 112 extending axially outwardly from body 86' in a slightly divergent relation and joined together at their inner ends to form a cup-shaped cavity 114.
  • Inner flange 110 is inclined or has an inclined lower surface, similar to flange 62 in FIG. 3, and the inner edge of flange 1 10 has an interference fit with rod 14' to wiper the same and thereby function in the same manner as wiper of FIG. 1.
  • rod wiper portion of member 56' can be identical to wiper 50, except that it is molded as part of seal member 56'.
  • This form of the invention is suitable for lighter duty applications and is more economical than the separate sealing and rod wiper arrangement of FIG. 2.
  • body 86' can be axially elongated as shown in FIG. 10 to increase the area of the inner bearing surface 115 thereof which is a generally cylindrical, axial surface like that shown at 92 in FIG. 4 but considerably elongated. This increases the bearing capability of seal member 56', and makes it possible to eliminate the separate sleeve bearing of FIG. 2 in lighter duty applications, thereby realizing further savings in cost.
  • sealing members 54 and 56 can be slid axially over rod 14 into the annular cavity 116 provided in a casing 118 and held in place against an abutment shoulder 120 provided on a cartridge nut 122 threaded on the end of casing 118 and fixed in place by means of a set screw 124.
  • Member 56' is formed of the same material as member 56 first described and is operative in conjunction with member 54 in the same manner as member 56, being otherwise identical thereto.
  • an improved composite seal having a pair of annular sealing members disposed in a side by side relation, said members being formed of materials having different hardnesses.
  • the softer member effectively seals under low pressure conditions and has total memory and a quick response. Under high pressure conditions, the softer member moves axially toward the harder member and is stretched radially whereby the frictional force acting between the softer member's sealing lip and the rod is relieved. The softer member also loads the harder member to increase the bearing pressure of its sealing lip against the rod. Extrusion of the softer member is prevented by the increased pressure imparted to the harder members sealing lip.
  • the composite seal of the present invention is leak-proof and has the capability of accommodating severe rod deflection thereby increasing the useful life thereof.
  • a composite seal for piston rods and the like comprising: a first annular member and a separate second annular member disposed in an axial abutting relation and captively retained about the outer surface of a relatively reciprocating member, said first and second annular members having portions, respectively, in sealing engagement with said reciprocating member, said first annular member being formed of a synthetic plastic material and said second annular member being formed of a synthetic plastic material of a higher durometer rating than said first member, said first annular member comprising a body terminating in an annular end face and said second annular member comprising a body having an annular abutment shoulder intermediate the opposite ends thereof facing said first member end face in axially spaced relation thereto under low pressure conditions, said members having coacting surfaces causing said first member to move relative to said second member under high pressure conditions with said first member end face approaching said second member shoulder and also causing said first annular member to be stretched radially outwardly thereby relieving the frictional force between said sealing engagement portion of said first member and the outer surface of said reciprocating
  • a composite seal according to claim 2 in combination with an hydraulic actuator having a hollow cylindrical member encircling said reciprocating member, said hollow member having an annular wall cavity confining said seal with said first flange in sealing engagement with said reciprocating member and said second flange in sealing engagement with the cavity wall, said annular groove facing the high pressure side of said actuator.
  • said wiping means comprises a first annular flange extending generally axially from said second annular member in a direction away from said first annular member and adapted to wipe said reciprocating member.
  • said wiping means includes a second annular flange extending generally axially from said second annular member in a direction away from said first annular member, said flanges being spaced apart radially thereby defining an annular groove therebetween, the spacing between said flanges increasing gradually in an axial direction from said second annular member, said first flange extending axially beyond said second flange.
  • a composite seal according to claim 13 wherein said second annular member has an inner wall comprising a straight portion parallel to the axis of said second annular member, and an inclined portion extending from said straight portion in a direction slightly radially inwardly thereof and terminating in a lip in fluid sealing engagement with the outer surface of said reciprocating member.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
US00108279A 1971-01-21 1971-01-21 Composite seal Expired - Lifetime US3765690A (en)

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US10827971A 1971-01-21 1971-01-21

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JP (1) JPS4861847A (de)
CA (1) CA963031A (de)
DE (1) DE2144681A1 (de)
GB (1) GB1369258A (de)

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4231578A (en) * 1979-04-23 1980-11-04 W. S. Shamban & Co. Seal assembly
US4252331A (en) * 1978-07-01 1981-02-24 Robert Bosch Gmbh Sealing arrangement
US4268045A (en) * 1979-04-23 1981-05-19 W. S. Shamban & Co. Seal assembly
US4269802A (en) * 1976-03-17 1981-05-26 Caterpillar Tractor Co. Process for making dual-material self-bonding lip seal
US4342463A (en) * 1980-10-16 1982-08-03 Green, Tweed & Co., Inc. Spring seal
US4380342A (en) * 1980-09-22 1983-04-19 Vought Corporation Fluid sealing devices
US4421330A (en) * 1982-02-08 1983-12-20 Greene, Tweed & Co., Inc. Antifriction fluid seal assembly
WO1984002967A1 (en) * 1983-01-19 1984-08-02 Swagelok Co Coupling
US4570944A (en) * 1985-05-15 1986-02-18 W. S. Shamban & Company Seal assembly with reduced wear low pressure sealing ring
US4807890A (en) * 1985-10-15 1989-02-28 Esco Elevators, Inc. Sealing combination
DE3738512A1 (de) * 1987-11-13 1989-05-24 Kugelfischer G Schaefer & Co Dichtung, vorzugsweise fuer hydraulische anlagen
US4893823A (en) * 1988-12-21 1990-01-16 Greene, Tweed & Co. Seal assembly
US4945724A (en) * 1989-01-26 1990-08-07 Cincinnati Milacron Inc. Apparatus for collecting hydraulic leakage fluid
WO1991010088A1 (en) * 1989-12-28 1991-07-11 W.S. Shamban & Company Spring energized seal assembly
US5542682A (en) * 1995-03-27 1996-08-06 American Variseal Slant coil spring and seal
FR2816024A1 (fr) * 2000-10-28 2002-05-03 Mannesmann Sachs Ag Joints d'etancheite primaires pour des systemes a cylindres emetteur/recepteur
US20020176791A1 (en) * 2001-05-23 2002-11-28 Yoshinori Uera Leakproof pump for use in an inking mechanism of a rotary printing press
US20040119280A1 (en) * 2002-12-20 2004-06-24 Zbigniew Kubala Fluid coolant union
US6758478B1 (en) * 2003-01-10 2004-07-06 Delphi Technologies, Inc. Elastomeric seal anti-extrusion wedge backup ring and flange
AU2002237265B2 (en) * 2001-01-19 2004-07-08 Aloys Wobben Ring-shaped seal
US20040195780A1 (en) * 2003-04-03 2004-10-07 Jeff Baehl Back pumping seal assembly
US20060066058A1 (en) * 2004-09-24 2006-03-30 Greene, Tweed Of Delaware, Inc. Cammed seal assembly with elastomeric energizer element
US20070273106A1 (en) * 2003-10-16 2007-11-29 Kaoru Nomichi Gas Seal Structure
US20080018059A1 (en) * 2004-12-28 2008-01-24 Nok Corporation Sealing Device
US20090108538A1 (en) * 2007-10-24 2009-04-30 Freudenberg-Nok General Partnership Two-Component Seal With Integral Locking Feature To Prevent Relative Rotation
US20100072708A1 (en) * 2008-09-19 2010-03-25 Engineering Design Resources Ltd. Seal assembly
US20100300823A1 (en) * 2007-12-18 2010-12-02 Vhit S.P.A. Unipersonale valve for the braking balancement, for a farm tractor or a similar vehicle
US20110140366A1 (en) * 2008-08-11 2011-06-16 John Crane Uk Limited Improvements in and relating to spring energised plastic seals
CN103174873A (zh) * 2011-12-21 2013-06-26 韦特柯格雷公司 阀排放冗余杆密封系统
US20150042048A1 (en) * 2012-01-20 2015-02-12 Uhde High Pressure Technologies Gmbh Support ring arrangement for a high-pressure seal
US9249797B2 (en) 2010-12-16 2016-02-02 S.P.M. Flow Control, Inc. Plunger packing with wedge seal having extrusion recess
US9746080B2 (en) 2014-10-31 2017-08-29 Aps Technology, Inc. High pressure seal assembly for a moveable shaft
US9897215B2 (en) 2012-12-31 2018-02-20 Vetco Gray Inc. Multi-valve seat seal assembly for a gate valve
US9976413B2 (en) 2015-02-20 2018-05-22 Aps Technology, Inc. Pressure locking device for downhole tools
US10221848B2 (en) 2015-07-02 2019-03-05 S.P.M. Flow Control, Inc. Valve for reciprocating pump assembly
US20210231183A1 (en) * 2020-01-23 2021-07-29 Hyundai Mobis Co., Ltd. Brake apparatus for vehicle
US11448210B2 (en) 2015-07-02 2022-09-20 Spm Oil & Gas Inc. Valve for reciprocating pump assembly

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DE2630499C2 (de) * 1976-07-07 1983-08-11 Kempchen & Co Gmbh, 4200 Oberhausen Dichtungsanordnung für einen in eine Deckelaufnahme eingesetzten Deckel
US4509764A (en) * 1981-11-12 1985-04-09 Skf Kugellagerfabriken Gmbh Sealing arrangement
US4537422A (en) * 1983-10-07 1985-08-27 Ex-Cell-O Corporation Sealing system for road wheel suspension
JPH0643578Y2 (ja) * 1986-12-29 1994-11-14 三菱電線工業株式会社 シールリング
DE3716862A1 (de) * 1987-05-20 1988-12-15 Blohm Voss Ag Anordnung zur abdichtung von rotierenden wellen
DE3817776A1 (de) * 1988-05-26 1989-12-07 Bauer Fritz & Soehne Ohg Gasfeder

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US2687335A (en) * 1950-03-15 1954-08-24 Hulie E Bowerman Piston
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US2914369A (en) * 1958-03-18 1959-11-24 Blackhawk Mfg Co Fluid seal
US3146683A (en) * 1961-09-19 1964-09-01 Alfred Teves K G Composite lubricating seal
GB1019523A (en) * 1964-01-22 1966-02-09 Angus George Co Ltd Improvements in and relating to packing rings
US3254898A (en) * 1963-06-21 1966-06-07 Trw Inc Multiple lip seal
US3271038A (en) * 1962-10-30 1966-09-06 Dowty Seals Ltd Sealing devices
US3606356A (en) * 1968-11-19 1971-09-20 Western Electric Co High-pressure seal assembly

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US2687335A (en) * 1950-03-15 1954-08-24 Hulie E Bowerman Piston
US2708573A (en) * 1952-07-10 1955-05-17 Wales Strippit Corp Seal for liquid springs
US2914369A (en) * 1958-03-18 1959-11-24 Blackhawk Mfg Co Fluid seal
US3146683A (en) * 1961-09-19 1964-09-01 Alfred Teves K G Composite lubricating seal
US3271038A (en) * 1962-10-30 1966-09-06 Dowty Seals Ltd Sealing devices
US3254898A (en) * 1963-06-21 1966-06-07 Trw Inc Multiple lip seal
GB1019523A (en) * 1964-01-22 1966-02-09 Angus George Co Ltd Improvements in and relating to packing rings
US3606356A (en) * 1968-11-19 1971-09-20 Western Electric Co High-pressure seal assembly

Cited By (56)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4269802A (en) * 1976-03-17 1981-05-26 Caterpillar Tractor Co. Process for making dual-material self-bonding lip seal
US4252331A (en) * 1978-07-01 1981-02-24 Robert Bosch Gmbh Sealing arrangement
US4231578A (en) * 1979-04-23 1980-11-04 W. S. Shamban & Co. Seal assembly
FR2455227A1 (fr) * 1979-04-23 1980-11-21 Shamban & Co W S Dispositif de joint d'etancheite
US4268045A (en) * 1979-04-23 1981-05-19 W. S. Shamban & Co. Seal assembly
US4380342A (en) * 1980-09-22 1983-04-19 Vought Corporation Fluid sealing devices
US4342463A (en) * 1980-10-16 1982-08-03 Green, Tweed & Co., Inc. Spring seal
US4421330A (en) * 1982-02-08 1983-12-20 Greene, Tweed & Co., Inc. Antifriction fluid seal assembly
WO1984002967A1 (en) * 1983-01-19 1984-08-02 Swagelok Co Coupling
US4570944A (en) * 1985-05-15 1986-02-18 W. S. Shamban & Company Seal assembly with reduced wear low pressure sealing ring
US4807890A (en) * 1985-10-15 1989-02-28 Esco Elevators, Inc. Sealing combination
DE3738512A1 (de) * 1987-11-13 1989-05-24 Kugelfischer G Schaefer & Co Dichtung, vorzugsweise fuer hydraulische anlagen
US4893823A (en) * 1988-12-21 1990-01-16 Greene, Tweed & Co. Seal assembly
US4945724A (en) * 1989-01-26 1990-08-07 Cincinnati Milacron Inc. Apparatus for collecting hydraulic leakage fluid
WO1991010088A1 (en) * 1989-12-28 1991-07-11 W.S. Shamban & Company Spring energized seal assembly
US5542682A (en) * 1995-03-27 1996-08-06 American Variseal Slant coil spring and seal
FR2816024A1 (fr) * 2000-10-28 2002-05-03 Mannesmann Sachs Ag Joints d'etancheite primaires pour des systemes a cylindres emetteur/recepteur
US6712362B2 (en) * 2000-10-28 2004-03-30 Mannesmann Sachs Ag Primary seals for master-slave cylinder systems
AU2002237265B2 (en) * 2001-01-19 2004-07-08 Aloys Wobben Ring-shaped seal
US20020176791A1 (en) * 2001-05-23 2002-11-28 Yoshinori Uera Leakproof pump for use in an inking mechanism of a rotary printing press
US20070228723A1 (en) * 2002-12-20 2007-10-04 Deublin Company Fluid coolant union
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Also Published As

Publication number Publication date
DE2144681A1 (de) 1972-08-17
JPS4861847A (de) 1973-08-29
GB1369258A (en) 1974-10-02
CA963031A (en) 1975-02-18

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